Pressure applying arrangement for a multiple flow machine

ABSTRACT

A multiple flow fluid handling machine of the radial piston type includes a rotor having a rotor end face, and two sets of working chambers connected by rotor passages with two sets of control ports on the rotor end face. The sets of rotor ports are spaced the same radial distance from the rotor axis. A stationary element has inlet and outlet passages, and control ports on a stationary end face. The control ports cooperate with the rotor ports, and are spaced from the rotor axis the same radial distance as the rotor ports. Control means press either the rotor with the rotor end face against the stationary end face, or press the stationary element with its stationary end face against the rotor end face. In the first case, control pistons in control cylinders of the rotor move the rotor axially, and in the second case, pressure fluid enters pressure chambers to urge the stationary element, which has portions in the pressure chambers, with the end face thereof against the rotor end face.

United States Patent 1 Eickmann [451 Jan. 28, 1975 PRESSURE APPLYING ARRANGEMENT FOR A MULTIPLE FLOW MACHINE Primary Examiner-William L. Freeh [76] Inventor Karl Eickn'mnn 2420 lsghiki Attorney, Agent, or FirmMichael S. Striker Hayama-machi, Kanagawa-ken, Japan 57 ABSTRACT [22] Filed: Mar. 24, 1972 I A multiple flow fluid handling machine of the radial PP N04 237,617 piston type includes a rotor having a rotor end face. and two sets of working chambers connected by rotor [30] Foreign Application priority Data passages with two sets of control ports on the rotor A r 7 1971 Aumia 2986/71 end face. The sets of rotor ports are spaced the same radial distance from the rotor axis. A stationary ele- .[52] U S Cl 91/487 91/492 ment has inlet and outlet passages, and control ports [5 H Folb 13/06 on a stationary end face. The control ports cooperate [58] Field 91/487 485 491 with the rotor ports, and are spaced from the rotor axis the sameradial distance as the rotor ports. Con- 56] Refe e ces Cited trol means press either the rotor with the rotor end I r n face against the stationary end face, or press the sta- UNITED STATES PATENTS t tionary element with its stationary end face against the 2,608,934 9/1952 Ferris 91/492 rotor end face. In the first case,,control pistons in con- 3 4 7/1959 y1 trol cylinders of the rotor move the rotor axially, and 3,066,613 l2/l962 Relnke 91/485 in the Second I Case, pressure fluid enters pressure gf chambers to urge the stationary element, which has g' g 8/1968 :32 :65 91/485 portions in the pressure chambers, with the end face 3 56l 328 2/1971 EichmannI:::.................:::: 91 497 thereof against the rotor end FOREIGN PATENTS OR APPLICATIONS 2 Chims, 3 Drawing Figures l,8l6,662 7/1970 Germany 91/492 BACKGROUND OF THE INVENTION The present invention relates to a pressure applying arrangement in multiple flow machines, such as hydraulic or pneumatic pumps, compressors, motors, transmissions or the like, having a plurality of sets of working chambers in which pistons or vanes are mounted for expanding or contracting the working chambers. Rotary fluid handling machines of this type are well known, and have been proved reliable. An apparatus of this type is disclosed in my US. Pat. No. 3,898,698. Known apparatus of this type has thedisadvantage that the structure is not compact enough, and that production costs are comparatively high, and that the efficiency should be improved.

SUMMARY OF THE INVENTION It is one object of the invention to overcome the disadvantages of known multiple flow hydraulic machines of this type, and to provide a multiple flow machine of high efficiency and highest possible output, while requiring little space.

Another object of the invention is to provide a machine of this type which can be inexpensively manufactured, and consist of simple parts so as to be reliable when extensively operated.

A double axial flow fluid handling machine in accordance with the invention has first and second bodies provided with first and second end faces and being movable relative to each other in axial direction to a limited extent. One of the bodies has two sets of separate working chambers in which displacement members are operable by actuator ring means to increase and reduce the volume of the working chambers. One of the bodies is associated with control means by which the end of one body is pressed against the end face of the other body, and the other body has control ports for supplying and discharging fluid from the first body. It is important that the rotor ports, which are spaced the same distance in radial direction from the axis of the rotor, cooperate with control ports which are spaced the same radial distance from the rotor axis.

In one embodiment of the invention, the body in which the working chambers are provided, serves as rotor and is mounted in bearings of a housing.

It is possible to provide a thrust bearing for supporting the rotor at one end, which is removed from the rotor end face. A housing portion has pressure chambers in which portions of the stationary body are located so that the stationary body can be pressed with its stationary end face against the rotor end face.

In another modification, the stationary body has inlet means and outlet means and control ports on its stationary end face, while the rotor has at the end remote from the rotor end face, control chambers in which axially movable control pistons are arranged which are supported on a thrust bearing, and cause movement of the rotor toward the stationary end face when pressure fluid from the working chambers enters the control cylinders. Due to the improvements of the invention, a double axial flow machine of simple construction, but operating at high efficiency, is obtained.

The novel features which are considered as characteristic for the invention are set forth in particular in the appended claims. The invention itself, however, both as to its construction and its method of operation, together with additional objects and advantages thereof, will be best understood from the following description of specific embodiments when read in connection with the accompanying drawing.

BRIEF DESCRIPTION OF THE DRAWING FIG. 1 is an axial sectional view illustrating one embodiment of the invention;

FIG. 2 is an axial sectional view illustrating another embodiment of the invention; and

FIG. 3 is an endview of a part of the machine of FIG. 1.

DESCRIPTION OF THE PREFERRED EMBODIMENTS In the embodiment of FIG. 1, a rotor 1 is mounted in bearings 16 and 15 in the stationary housing of the machine. Rotor 1 has two sets of working chambers 3.and 4, the sets being axially spaced from each other. Displacement elements, shown to be pistons 5, are mounted in the working chambers 3 and 4 for radial movement, but could be replaced by vanes. The outer ends of the displacement elements 5 cooperate with an actuator guide ring, not shown, by which they are displaced in the working chambers during rotation of rotor l, as is known to those skilled in the art.

In accordance with the invention, rotor 1 has rotor passages 13 and 14 extending substantially in axial direction, and being connected with the working chambers 3 and 4, respectively. In accordance with the invention, the rotor passages 13 of the set of working chambers 3, and also the rotor passages 14 of the working chambers 4 extend in the same axial direction to the same control face 31 of rotor l in which the rotor passages 13 and 14 open in rotor ports. It is also a feature of the invention that the rotor passages 13 and. 14, and the respective rotor ports, are spaced the same radial distance from the rotor axis of rotor 1, and sweep corresponding control ports of passages 16 and 17 in a control part 6, the control ports in the stationary control face 32 being spaced the same radial distance from the rotor axis as the rotor ports.

Part 6 has an eccentric portion 44 with an outer cylinder surface 42 which is eccentric to the rotor axis and is located in sealing and sliding contact with a pressure chamber 8 in a stationary housing part 2. Rotor l is supported by an annular bearing 16 for rotation in housing part 2, and also abuts a thrust bearing 15 which abuts a housing portion 2a so that rotor 1 cannot move to the right as viewed in FIG. 1.

Another pressure chamber 9 has a cylindrical surface 43 concentric with the rotor axis, and a cylindrical portion of part 6 is located in pressure chamber 9 having a cylindrical surface fitting into the inner cylindrical surface 43 in sliding and sealing engagement.

The pressure chambers 8 and 9 communicate with inlet and outlet means 10, 11 so that pressure is applied in the pressure chambers 8 and 9 to move part 6 with its end face 32 toward the rotor end face 31. Chamber 45 at the end of part 6 is not connected to pressure fluid, but may be connected to the atmosphere. The cylindrical surfaces 41, 42, 43 seal the pressure chambers 8 and 9. The cylindrical sealing surface 42 is eccentric to the axis of the rotor.

The fluid-containing pressure chambers 8 and 9 are staggered relative to each other in axial and in radial directions. The sealing surface 42 is also eccentric. The pressure chamber 8 is formed between the sealing surface 41 and the eccentric sealing surface 42. The pressure chamber 9 is formed between the centric sealing surface 43 and the eccentric sealing surface 42.

In the pressure body 6, inlet and outlet passages 12 and 7 are provided which end in control ports 16 and 17 on the stationary end face 32. The inlet and outlet means 10 and 11 provide fluid for the passages 12 and 7. The passage 12 connects the inlet means 10 through the pressure body 6 with the control port 16, while the passage 17 connects the outlet means 11 through pressure body 6 with the control port 17. An endless surface portion of the control face 32 of pressure body 6 surrounds the inlet and outlet passages 12 and 17, as shown in FIG. 3, and is larger than effective pressure area at one of the ports of the passages 12 and 17.

The pressure body 6 is movable in axial direction to a limited extent due to the sliding engagement between the cylindrical outer surfaces of the pressure body 6 with the inner cylindrical surfaces of the housing part 2. When fluid of high pressure enters the pressure chambers 8 or 9, fluid pressure is exerted by the pressure chambers against the pressure member 6 so that the same is moved axially with its end face 32 toward the rotor end face 31 so that between pressure part 6 and rotor l a sealing contact is obtained, and the ports in end faces 31 and 32 can communicate with a minimum leakage.

During the operation of the machine, fluid flows from inlet means 10 through the inlet passage 12 and the control port 16, as well as through the rotor passages 13 and 14 into the working chambers 3 and 4 and out of the same into the respective rotor passages 13 and 15 through control port 17 and outlet passage 7 into the outlet means 11, but the direction of flow of fluid may be reversed. In accordance with the invention, the rotor passages 13 and 14 of the two sets of rotor working chambers 3 and 4 are spaced in radial direction substantially the same distance from the rotor axis as are the control ports 16 and 17 spaced from the rotor axis so that the rotor ports 13 and 14 communicate with the control ports 17 and 16, and register with the same. In this manner, a double flow machine with separate sets of working chambers 3 and 4 can be controlled by means of the pressure body 6 as easily as a single flow machine.

The eccentricity, that is the radial distance e between the axis of the cylindrical surface 42 and the rotor axis, and also the diameters of the sealing surfaces 41 and 43, must be selected so that the pressure acting in the fluid containing pressure chambers 8 or 9, presses the pressure body 6 with the required, but not exceeded force toward the rotor face 31 of rotor 1 so that the control face 32 is in sealing contact with the rotor face 31 without excessive friction.

Due to the positioning of the rotor passages 13 and 14 at the same radial distance from the rotor axis, it is possible to use in double flow machines the reliable pressure body 6 with pressure chambers 8 and 9, whose reliability has been proven by use with single flow machines.

In the embodiment of the invention shown in FIG. 2, the rotor 1 is again provided with two axially spaced sets of working chambers 3 and 4 forming cylinders for the radially reciprocating pistons 5. Rotor 1 is supported in annular bearing 16 which is mounted on the housing, part of which is the body 2, and the end portion 2a. The body 2 has a stationary control face 32 on which the rotor end face 31 abuts in sliding contact. Body 2 has inlet and outlet means 10, 11 and inlet and outlet ports 16, 17 which are spaced the same radial distance from the rotor axis as the rotor ports 14 and 13 on the rotor end face 31. Rotor passages, which are parallel to the axis, connect the rotor ports 13 and 14 with the working chambers 3 and 4.

In the embodiment of FIG. 2, the body 2 is stationary also in axial direction, and the rotor ports 13 and 14 successively pass the control ports 16 and 17 to connect the working chambers 3 and 4 with the inlet means and outlet means 10, 11.

Each working chamber 3 is connected by a control passage 21 with a control cylinder 22, and each working chamber 4 is connected by a control passage 24 with a control cylinder 25. Control cylinders 22 and 25 are open at the end of the rotor part 1 remote from rotor end face 31, and control pistons 23 and 26 are respectively located in the control cylinders 22, 25 and have free projecting ends abutting a thrust anti-friction bearing 15 which is supported on the stationary housing part 2a against axial displacement. The thrust bearing 15 permits rotation of control pistons 23, 26 with rotor part 1, but blocks axial movement of control pistons 23, 26, so that pressure in the control cylinders 22, 25 urges rotor part 1 toward the stationary part 2.

During rotation of rotor 1, pressure fluid from the working chambers 3 and 4 is supplied through control passages 21 and 24 to the control cylinders 22 and 25. During half a revolution of the rotor, low pressure prevails in the control cylinders 22 and 25, and during the other half revolution, high pressure prevails in the control cylinders 22 and 25, depending on whether high pressure or low pressure is present at the control port 16 or at the control port 17 in the stationary face 32.

The high pressure or low pressure in the control cylinders 22, 25 urges rotor 2 to the left as viewed in FIG. 1 so that the rotor end face 31 with rotor ports 13, 14 is pressed against the stationary end face 32 with control ports 16 and 17 so that the rotor end face 31 slides on the stationary end face 32 in sealing contact.

The fluid flows through the machine from inlet means 10 through control passage 16 and a rotor port 14 or 13 into working chamber 4 or 3, and then out of working chamber 4 or 3 through rotor ports 14 or 13 through the control ports 17 and outlet means 11. The varying pressures in the working chambers 3 and 4 also prevail in the control cylinders 22 and 25, and at the rotor ports 13 and 14, so that the pressure at the end faces 31 32 is compensated by the pressures acting on the rotor in the control cylinders 22 and 25.

In both embodiments of the invention, first and second bodies cooperate by means of end faces 31 and 32. The first body is the rotor 1, and the second body is either the body 6 in the embodiment of FIG. I, or the body 2 in the embodiment of FIG. 2. Control means are provided, in FIG. 1 in the form of member 2 with pressure chambers 8 and 9, and in the embodiment of FIG. 2 in the form of control pistons 22, 26 in control cylinders 22, 25, the control pistons being supported by the thrust bearing 15'.

In the embodiment of FIG. 1, the cylindrical portion 44 of control part 6 and the pressure chambers 8 and 9 are important features of the invention in connection with the arrangement of the ports 13, 14, 16 and 17 along a common circle about the rotor axis. In the embodiment of FIG. 2, the control cylinders 22, 25, the

control pistons 23, 26, and the control passages 21 and 24, together with the arrangement of the ports l3, l4, l6 and 17 along a common circle having its center in the outer axis, are important features of the invention.

It will be understood that each of the elements described above, or two or more together, may also find a useful application in other types'of multiple flow machines differing from the types described above.

While the invention has been illustrated and described as embodied in a pressure applying arrangement for a multiple flow fluid handling machine, it is not intended to be limited to the details shown, since various modifications and structural changes may be made without departing in any way from the spirit of the present invention.

Without further analysis, the foregoing will so fully reveal the gist of the present invention that others can by applying current knowledge readily adapt it for various applications without omitting features that, from the standpoint of prior art, fairly constitute essential characteristics of the generic or specific aspects of this invention and, therefore such adaptations should and are intended to be comprehended within the meaning and range of equivalence of the following claims.

What is claimed as new and desired to be protected by Letters Patent is set forth in the appended claims.

I claim:

1. In a multiple flow machine, in combination, a pressure applying arrangement comprising at least first and second bodies having first and second end faces abutting each other, said first body being a rotor rotatable about an axis, and said second body being nonrotatable, said first body having two spaced sets of working chambers and two sets of rotor passages connected with said sets of working chambers, respectively, and opening on said first end face in rotor ports spaced from said axis the same radial distance; said second body having inlet and outlet passages opening in control ports on said second end face thereof spaced from said axis the same radial distance as said rotor ports so that during rotation of said first body said rotor ports communicate through said control ports with said inlet and outlet passages; said second body being mounted for limited axial movement relative to said first body and having cylindrical portions; and control means for pressing said second body with the end face thereof against the end face of said first body, said control means including a stationary housing portion having inlet and outlet means, and pressure chambers communicating with said inlet and outlet means and having cylindrical inner surfaces, said cylindrical portions of said second body slidingly and sealingly fitting into associated pressure chambers so that the pressure in said pressure chambers presses said second body with said second end face thereof against said first end face of said first body, at least one of said pressure chambers and associated cylindrical portions of said second body being centric to said axis, and at least one other of said pressure chambers and cylindrical portions of said second body being eccentric to said axis, said second body having in said second end face, a central end bore, arcuate inlet control ports and outlet control ports, and an endless uninterrupted face portion surrounding said inlet control ports and outlet control ports, and extending between said central bore and the radially outer end of said second end face, the cross sectional effective area of each of said pressure chambers being larger than the corresponding effective pressure area along one of said ports and said end face.

2. In a multiple flow machine, in combination a pressure applying arrangement comprising at least first and second bodies having first and second end faces abutting each other, said first body being a rotor rotatable about an axis, and said second body being nonrotatable, said first body having two spaced sets of working chambers and two sets of rotor passages connected with said sets of working chambers, respectively, and opening on said first end face in rotor ports spaced from said axis the same radial distance; said second body having inlet and outlet passages opening in control ports on said second end face thereof spaced from said axis the same radial distance assaid rotor ports so that during rotation of said first body said rotor ports communicate through said control ports with said inlet and outlet passages; said first body being mounted for limited axial movement relative to said second body; and control means for pressing said first body with the end face thereof against the end face of said second body, said second body having inlet means and outlet means communicating with said inlet and outlet passages, respectively, said first body having two sets of control passages extending parallel to said axis communicating with said two sets of working chambers, and axial control cylinders at the end of said first body remote from said first end face, and communicating with the ends of said sets of control passages, each control passage of one of said two sets of control passages communicating with one working chamber of one of said two sets of working chambers, and each control passage of the other set of control passages communicating with one working chamber of the other of said two sets of working chambers, each control passage of one of said two sets of control passages being located between two control passages of the other set of said sets of control passages; said control means including control pistons slidingly engaging said control cylinders in axial direction and thrust bearing means including an annular ball bearing supporting said control pistons against axial movement out of said control cylinders so that the pressure in said-working chambers acts in said control cylinders to move said first body away from said control pistons and said thrust bearing means whereby said first end face is pressed against said second end face. 

1. In a multiple flow machine, in combination, a pressure applying arrangement comprising at least first and second bodies having first and second end faces abutting each other, said first body being a rotor rotatable about an axis, and said second body being non-rotatable, said first body having two spaced sets of working chambers and two sets of rotor passages connected with said sets of working chambers, respectively, and opening on said first end face in rotor ports spaced from said axis the same radial distance; said second body having inlet and outlet passages opening in control ports on said second end face thereof spaced from said axis the same radial distance as said rotor ports so that during rotation of said first body said rotor ports communicate through said control ports with said inlet and outlet passages; said second body being mounted for limited axial movement relative to said first body and having cylindrical portions; and control means for pressing said second body with the end face thereof against the end face of said first body, said control means including a stationary housing portion having inlet and outlet means, and pressure chambers communicating with said inlet and outlet means and having cylindrical inner surfaces, said cylindrical portions of said second body slidingly and sealingly fitting into associated pressure chambers so that the pressure in said pressure chambers presses said second body with said second end face thereof against said first end face of said first body, at least one of said pressure chambers and associated cylindrical portions of said second body being centric to said axis, and at least one other of said pressure chambers and cylindrical portions of said second body being eccentric to said axis, said second body having in said second end face, a central end bore, arcuate inlet control ports and outlet control ports, and an endless uninterrupted face portion surrounding said inlet control ports and outlet control ports, and extending between said central bore and the radially outer end of said second end face, the cross sectional effective area of each of said pressure chambers being larger than the corresponding effective pressure area along one of said ports and said end face.
 2. In a multiple flow machine, in combination a pressure applying arrangement comprising at least first and second bodies having first and second end faces abutting each other, said first body being a rotor rotatable about an axis, and said second body being non-rotatable, said first body having two spaced sets of working chambers and two sets of rotor passages connected with said sets of working chambers, respectively, and opening on said first end face in rotor ports spaced from said axis the same radial distance; said second body having inlet and outlet passages opening in control ports on said second end face thereof spaced from said axis the same radial distance as said rotor ports so that during rotation of said first body said rotor ports communicate through said control ports with said inlet and outlet passages; said first body being mounted for limited axial movement relative to said second body; and control means for pressing said first body with the end face thereof against the end face of said seCond body, said second body having inlet means and outlet means communicating with said inlet and outlet passages, respectively, said first body having two sets of control passages extending parallel to said axis communicating with said two sets of working chambers, and axial control cylinders at the end of said first body remote from said first end face, and communicating with the ends of said sets of control passages, each control passage of one of said two sets of control passages communicating with one working chamber of one of said two sets of working chambers, and each control passage of the other set of control passages communicating with one working chamber of the other of said two sets of working chambers, each control passage of one of said two sets of control passages being located between two control passages of the other set of said sets of control passages; said control means including control pistons slidingly engaging said control cylinders in axial direction and thrust bearing means including an annular ball bearing supporting said control pistons against axial movement out of said control cylinders so that the pressure in said working chambers acts in said control cylinders to move said first body away from said control pistons and said thrust bearing means whereby said first end face is pressed against said second end face. 